Grinder for valve decks of pumps



March 20, 1956 BLAGG GRINDER FOR VALVE DECKS OF' PUMPS 3 Sheets-Sheet l Filed April l, 1954 linux) 66 F'G. l.

A TTORNEK March 20, 1956 BLAGG GRINDER FOR VALVE DECKS OF PUMPS 3 Sheets-Sheet 2 Filed April l, 1954 K ,M m.. R ma m uw. r A mme nM 0 e L YnV Bv March 20, 1956 1 BLAGG 2,738,627

GRINDER FOR VALVE DECKS OF PUMPS Filed April l, 1954 3 Sheets-Sheet 3 4 0, l wA/'r supp/y F' l G. 4. 40

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2,738,627 V Y `GRINDER Fon VALVE DEcKs oF rUMrs Leon Blagg, Houston, Tex., assignor, by `mesne assignments, to Esso Research and Engineering Company, Elizabeth, N. J., a corporation of Delaware `Aplilication April 1, 19754, Serial No. 420,389 3 Claims. (Cl. 51-245) ing force; Y

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B and base A are concentric. However, body B is'provided with a central passage whichnis eccentric with regard to body'B and arranged within passage 25 is the drive shaft assembly E.v Thus, when body B rotates, drive shaft assembly E carried thereby is given orbital movement. p

Housing C consists of cap member 26, cylindrical spacing member 27, ring gear member 28, and annular shaped member 29, these members being secured together by means of bolts 30. Annular member 29 has its outer surface provided with screw threads 31 which mate with corresponding screw threads 32 of base A. The inner circular surface v33 of member 29 is provided with an inwardly extending circular ledge 34. Ledge 34 is slidable with respect to member 20 and ring 23 of rotatable body B so that rotatable body B may rotate while housing C remains stationary; however, rotatable body B cannot move axially with regard to housing C. The space between the outer shoulder of member 21 of body B and cap 26 of housing C is sealed by seal 35. Handles 36 are mounted on cap member 26 of. housing C for convenience in handling and also for Fig. 2 is a view taken along the line 2-2Iof Figfl; 25

. Fig. 3 is a view taken along the line 3-.3 of Fig. l; Fig. 4 is in the form of an elevation of the embodiment of Figs. 1 to 3, inclusive, shown in position `for grinding the valve deck of a pump body; p

Fig. 5 is a view showing details of construction of a portion of the assembly of Figs. 1 to 4 inclusive;

Fig. 6 is a fragmentary view taken along line 6'-6 0f Fig.' 4 illustrating the movement of the grinding wheel in relation to the surface of the valve deck; and,

convenience in allowing an operator to give housing C angular motion. With screw threads 31 and 32 engaged, as seen in Fig. 1 of the drawing, rotation of housing C causes it to move axially with regard to base A.

Asshown more clearly in Fig. 4, base A is provided with a scale 37 and housing C is provided with an index or pointer 38. If desired, the position of the scale and housing may be reversed with the scale placed on hous ingC and the index onbase A. In any event, base A and housing C cooperate to provide scale and index means.

Fig. 7 is in the form of an elevation partly in section 35 showing the grinding mechanism mounted on a xture for dressing the'grinding wheel to the proper taper.

In Fig. 1 particularly the principal parts ofthe grinder consist of a cylindrical base A, cylindrical rotatable body B, cylindrical housing C, prime mover D, cylindrically shaped drive shaft assembly E, gear Atrain F and grind- Since rotatable body B is mounted on housing C for rotatable movement but is held against axial movement, the axial movement of both housing C and supported rotatable body B with regard to base A may be adjusted as1desired by the operators changing the axial position ing assembly G. In Fig. 4 the grinder is shown mounted in pump .body H and in Fig. 7 the grinder; is shown mounted in fixture J.

As will be seen by reference to Fig. 4, base A is provided with external screw threads 11 whichY mate with corresponding screw threads 12 of pump body H so that of housing C and the axial position of housing C as well as that of rotatable body B may be instantly determined by visual examination.

Prime mover D, as seen in Fig. 4, may be a conventional type. In the embodiment shown an air motor is illustrated with compressed air being supplied from a source not shown from hose 40 through a conventional rotary seal 40 to themotor As seen in Fig. 1, a portion of motor D is shown with motor body 41 attached p to the upper end of member 21 of rotatable body B by base A may be screwed into a known position inpump body H and may be removed therefrom and returnedv to this exact position. Base A is concentric with the surface 108 of the valve. Base A is provided with 'handles 13 for the convenience of an operator in moving the device and in placing it in a valve body or in a xture as desired. It will be understood that in some designs of pumps, instead of employing a single thread 12 to hold the valve cap down, studs are used and in such a case an adapter (not shown) may be provided to engage with screw threads 11 of body A, and in turn be fastened to pump body H by studs As shown in Fig. 1, base A is provided with a passage 14, one lend of which extends through the outer surface of the body and is provided with a` grease iitting 15 while its other end extends through the inner wall and discharges intona space between bronze bearings `16 and 17 to allow the introduction of lubricant between base A and rotatable body B.

vRotatable body B rconsists of a member 20 of a generally tubular shape with its upper end terminating in an outwardly extending flange, member21 of4 a generally tubular shape mounted on and secured to member 20 by `machine screws 22 and ring member 23 fastened to member 20 by screws 24. Rotatable body screw threads 42. The shaft 43 of motor D passes through a central opening in member 21 rotatable body B with a seal 44 providing a seal between body and shaft 43.

Drive shaft assembly E which transmits power from prime mover D to grinding assembly housing C consists of mandrel 50, worm gear 51, and shaft 52. As seen in the drawing, the upper end of mandrel 50 has a reduced section 53 which fits within the central passage of gear 51 and is keyed thereto by key 54. The lower end of shaft 52-extends into the ge'ar 51 and is valso keyed thereto by key 54, the gear 51 serving as a connection means between the mandrel 50 and shaft 52. The upper end of shaft 52 extends into a recess in the lower end of shaft 43 of motor D and is keyed thereto by key 56.

Drive shaft assembly E is mounted in body B for rotationwith respect to vbody B with bearing assemblies 57 and 58 supporting its upper end and bearing assemblies 59 and 60 supporting its lower end. The space between the upper portion of the mandrel and member 21 o f bodyv B is sealed by seal 61 and the space between thelower end of drive shaft assemblyv E and bodyB is sealed by,

a sealing assembly consisting `of sleeve 62 secured to, member 20 byscrew threads, sleeve 63 secured to man- 1- drel 50 by screw threads andlseal 64 arranged in a recess" in member 62 with its inner circular surface in contact with sleeve 63.

Mounted on the lower end of mandrel 50 of drive shaft assembly E is grinding assembly G consisting of conical grinding wheel 65 held in position by washers 66, -67 and nut 68.

The gear train assembly which causes body B to be given rotative movement from energy supplied by prime mover D is shown in Figs. l, 2, and 5. A supporting block 70 is secured to the upper lsurface of member 20 by cap screw 71. A shaft 72 is mounted for rotation and also for longitudinal movement on member 70 with a bevelled gear 73 secured to one end and a projecting circular shoulder 74 at its other end. A spring 75 fits into a suitable recess provided in block 70 and exerts a bias to the left on shaft 72 as seen in Fig. 5. Worm wheel 76 adapted to engage with the teeth of worm 51 is slidably mounted on shaft 72 and is keyed thereto for rotation therewith by ke'y 77. A shaft 78 is secured to the upper end of member 20 of assembly B and rotatably' mounted thereon is member 79 which has its upper end terminating in bevelledgear teeth 80 and its lower portion terminating in a pinion gear 81 which engages with the teeth of ring gea'r 28. A clutch for the gear train is provided by an L-shap'ed lever 82 pivoted by pivot 83 to block 70 and having its upper surface 84 in the form of a cam surface. A camming member 85 is secured to block '70 by cap Screw 88 and is provided with a cam surface 89 which cooperates with the cam surface 84 of member 82 and is provided withV a handle 90 which is outside of housing C as'4 seen in Figs- 1 and 4.

Astwill be seen in Fig. 5, t he gear train mayA be' disengaged. The bevelled gear 73 isA shown in its disengagedv position by dashed lines'. This disengagement results when the operator moves handley 90' in the clockwisevr direction as when looking downl on Fig. 5. This allows spring 75 to bias shaft 72 to the le'ft as seen yin Fig. 5,- which in turn moves bent lever arm' 82 to the left positionV as indicated by dashed lines in Fig. 5. This causes bevelled gear 73 to be drawn out of contact with bevel gear 80. Rotation of handle 90 inthe counterclockwise direction, as when looking down on Fig. forces bent lever arm 82 into its position as shown in?v fulllines in Fig. 5 by the cam Surface' 89'frictionally contacting cam surface 84 and pushing lever arm 82 which in turn forces shaft 72 to the right and locks it in the position shown by full' lines in this figure. Whenthe bevelled gears 73 and 80 are engaged, body B isV caused to rotate simul^ taneously with the' rotation` of drive shaftY assembly E but at a lower rate,` the rate depending upon the gear ratios used. A- satisfactory 'ratio has been found to be 100 revolutions of drivel shaft E for each revolution of body B and the' orbital speed of body B of about 60 R. l. M. The simultaneous rotation of body B and drive` shaft assembly E causesV grinding assembly Gf simultaneously to* rotate an`dfmove orbitally. The disen: ga'gement of bevell'ed gearsr 73 and 80 by the use ofthe clutch mechanism shown terminates" rotation of body B so' that the only movement'i given shaftassembly E and grinding assembly G is rotative movement.

The movement 4of tapered grinding member' 65 with respect to tapered interna-l surface 108 is indicated byy the showing in Fig. 6. In this figure the solid arrows indicate the rotation of member 65 with simultaneousorbital movement of shaftA 50;- possible paths of move-` ment' of member 65b`ein'g-indieated bythe dashedlines.

Thev proper taper' isgivenI grinding-.wheel 65 by the use' of fixture] shown iii-Figi?. As shown-in Fig. 7, fixture .i consists of body 100"y provided with` screw threads 101 identical to the screw'thre'ads 12 of the m'udpump body H as shown in Fig. 4. Carried by bo'dy`100 are4 'guide means 102 upon which' isslidably'arrangeda carriage y103 carrying a diamondv dressing-tool 104; Carriage 103 is' provide with a threaded .bore engaging'. with a traversing screw" 105 which is mounted' on" member 107v carriedA4 byl guides 4102 wtih the end of the screw being provided with a hand crank 109. It will be seen that the guide members 102 make an angle with the axis of the threaded opening 101, this angle being the exact angle required for the grinding wheel 65. By ones mounting the grinder in fixture G as shown in Fig. 7, then disengaging the clutch nmechanism so that body B remains stationary while drive shaft E and grinding assembly G rotate, the grinding wheel may be dressed to the exact taper desired. When the wheel dressing operation is carried out, base A is mounted in a known predetermined position on body 110 of fixture J. As material is removed from wheel 65 by diamond dressing tool 104, the wheel 65 must be lowered by rotation of housing C on base A. When the dressing operation is completed, the pointer 38 of housing C has been moved to some position on scale 33 of base A. For convenience, the pointer is then left in this position while base A is removed from fixture I4 and mounted in position on pump body G, as shown in Fig. 4. Thevv clutch assembly is then engaged so that operation of prime mover C causes grinding wheel 65 to progress as well as rotate. Since the grinding wheel 65 is tapered, the diameter it cuts will be increased as it is advanced me die valve deck, the desired diameter of tapered surface 108 being obtained by advancement of the wheel into the deck the desired axial distance.

1. A grinding device for grinding a conical surface for the valve deck of a pump comprising, in combination, a cylindrical base member having external screw threads for fastening lit in a fixed predetermined position on said concentric with the conical surface, a cylindrical housing including a peripheral ring gear concentric with'said base and mounted on said base for axial movement, said housing cooperating with said base to provide scale inf dexin'g means for indicating the axial position of said housing; a cylindrical body concentrically and rotatively carried by said housing, a first drive shaft rotatively mounted on said body with its axis eccentric with, the axis of s'aid body, a prime mover mounted on said body with a second drive shaft arranged to transmit rotative movement to the said first drive shaft, a conically surfaced grinding member secured to said rst drive shaft member and a gear train assembly arranged to transmit rotative' l movement from said first drive shaft to said ring gear whereby rotation of said prime mover causes simultaneousrotation ofv said first drive shaft and said body member to' givesaid'shaft and attached grinding member rotative and orbital movement.

2. A'A device in accordance with claim l in which said gear tram'z assembly includes a disengageable clutch adapted to" terminate rotation of body B when disengaged.

3. A grinder adapted for grinding an internal tapering surface for the'valve deck of a pump comprising, in corn-y bina'tion', a cylindrical base member provided withannular externl screw threads formed integrally therewith forv mounting vit in a predetermined fixed position onv said pump with itsa'xis concentric with the axis of the tapered internal surface, a cylindrical housing member carried by tlie base member concentric therewith and capping' said base member, said housing and said base member having annular mating screw threads to permit axial movement ofv saidf housing member along said base member, scale indexingv means provided by said base member and housing for indicating the axial position of said housing, a cylindrical body rotatably carried by said housing concentricwith said housing and said base, a drive shaft assembly rotatably mounted on said housing having an axiseccentr'i'cwith the axis of said body, a' prime mover mountecl on said housing having a motor shaft aligned W'itli and'rigidly connected to said drive shaft assembly',

a conically tapered grinding means carried by said shaft assembly, and gear means arranged to transmit power from said drive shaft assembly to said body to cause rotation of said body when said shaft assembly rotates whereby said grinding member is simultaneously given rotative and orbital movement.

References Cited in the le of this patent UNITED STATES PATENTS Garner Mar. 7, 1922 Gutenson Sept. 12, 1922 Schwakopf Jan. 2, 1934 Hall May 11, 1943 

1. A GRINDING DEVICE FOR GRINDING A CONCIAL SURFACE FOR THE VALVE DECK OF A PUMP COMPRISING, IN COMBINATION, A CYLINDRICAL BASE MEMBER HAVING EXTERNAL SCREW THREADS FOR FASTENING IT IN A FIXED PREDETERMINED POSITION ON SAID PUMP CONCENTRIC WITH THE CONICAL SURFACE, A CYLINDRICAL HOUSING INCLUDING A PERIPHERAL RING GEAR CONCENTRIC WITH SAID BASE AND MOUNTED ON SAID BASE FOR AXIAL MOVEMENT, SAID HOUSING COOPERATING WITH SAID BASE TO PROVIDE SCALE INDEXING MEANS FOR INDICATING THE AXIAL POSITION OF SAID HOUSING, A CYLINDRICAL BODY CONCENTRICALLY AND ROTATIVELY CARRIED BY SAID HOUSING, A FIRST DRIVE SHAFT ROTATIVELY MOUNTED ON SAID BODY WITH ITS AXIS ECCENTRIC WITH THE 